DE102022200954A1 - Drive for a door or a window - Google Patents

Abstract

The application relates to a drive for a door or window, comprising a housing, an output shaft rotatably mounted on the housing and having a cam disk, an electric motor with a gear for driving the output shaft from a closed position in an opening direction in order to close the door or window open, a roller that rolls on the rotating cam disk during operation, a pivoting lever that is articulated on the housing so that it can pivot about a pivot axis, the roller being arranged on the pivoting lever so that it can rotate, and an energy storage unit for driving the output shaft from an open position in a closing direction, to close the door or the window, wherein the energy storage unit has an energy storage device having a longitudinal axis and a movable first abutment facing the roller, as well as a second abutment facing away from the roller, on which the energy storage device is supported, the roller being force-transmitting between the cam disk and the movable first abutment of the energy storage unit, wherein the cam disk and the energy storage unit are arranged on opposite sides with respect to the pivoting lever, and wherein the movable first abutment of the energy storage unit is rotatably and non-displaceably coupled to the pivoting lever at a coupling point and is thereby separated from the pivoting lever is guided along a circular path.

Description

The invention relates to a drive for a door or a window and in particular to a motor-operated drive for a door or a window.

Such motor-operated drives, which can also be referred to as automatic drives, transmit at least part of the drive power of the drive motor, usually via a linkage, to a door or window sash in order to pivot it. A second part of the drive power can be transmitted to an energy store, which can be designed as a compression spring, via a cam disk mechanism. The cam disk mechanism comprises a cam disk located in a so-called cage. The cage is connected to a roller and the roller is arranged in such a way that the roller rolls on a peripheral surface of the cam disk. The cage is in turn connected to a tie rod and the tie rod is connected to the compression spring via a piston. When the door is opened using the drive, the cam disk is rotated. This moves the cage connected to the roller, the pull rod and the piston and consequently tensions the compression spring.

Due to the space required by the cage and the pull rod, the constructive connection of the motor-gear unit is complex and other components such as a bearing for the cage and the piston have little space. There is thus the difficulty that either a more compact bearing has to be used, which leads to higher friction and thus to a less powerful drive, or the entire drive has to be built larger and requires more installation space.

In addition, in the drive described above, the central axis of the output shaft is not aligned with the compression spring, so that bending moments act on the cage and the tie rod, which means that a particularly complex and cost-intensive construction is required to absorb the bending forces.

A further disadvantage of this design is that the design of the cage, its mounting and the connection of the pull rod to the cage and the piston are complex, which has a negative effect on the manufacturing costs of the drive.

In general, the numerous bearing points generate a lot of friction, which means that the efficiency of the drive needs to be improved. In addition, the high level of friction creates wear and, due to the higher drive torques required, means that larger and more expensive drive motors are required.

It is therefore an object of the present invention to provide a drive that is powerful, inexpensive and compact.

The object is achieved by a drive with the features of claim 1 and in particular in that the drive has a pivoted lever which is pivoted about a pivot axis on a housing, wherein the roller is arranged rotatably on the pivoted lever that an energy storage unit for driving the output shaft is provided from an open position in a closing direction in order to close the door or the window, the energy storage unit having an energy storage device having a longitudinal axis and a movable first abutment facing the roller and a second abutment facing away from the roller, on which the supports the energy store, has that the roller acts in a force-transmitting manner between the cam disk and the movable first abutment of the energy storage unit, that the cam disk and the energy storage unit are arranged on opposite sides with respect to the pivot lever, and that the movable first abutment of the energy storage unit can be rotated at a coupling point and non-displaceably coupled to the pivoted lever and is thereby guided by the pivoted lever on a circular path.

Coupled in a non-displaceable manner means that the first abutment cannot perform any linear movement relative to the pivoting lever.

A drive with these features has a simple structure with few friction losses, since only a few bearing points are required, since the first abutment can be guided and supported solely by the pivoting lever. In addition, the force of the energy store can be transmitted directly to the cam disk without the first abutment or the energy store coming into contact with the housing and causing friction losses. As a result, the drive can be operated with a high level of efficiency, which in turn means that the drive can be dimensioned to be compact and can be produced inexpensively.

The cam disk can be coupled to the output shaft in a rotationally fixed manner or can be formed in one piece with the output shaft. The cam disk can also be referred to as a cam disk or heart cam disk. Depending on the desired drive torque profile, the cam disk can have a symmetrical or asymmetrical outer contour. The output shaft can be rotatable in both directions of rotation from a rest position in order to ensure different types of installation.

Advantageous developments of the invention can be found in the dependent claims, the description and the drawing.

In general, a drive motor of the drive can be coupled to the output shaft via a gear. The gear can be designed as a spur gear, as a combination of worm gear and spur gear, as a combination of curved or spiral bevel gear and spur gear, or as a combination of hypoid gear or hypoid bevel gear and spur gear.

According to a particularly compact design, the gear comprises a worm gear and a spur gear.

According to a further embodiment, the electric motor and the energy storage unit are arranged on opposite sides with respect to the output shaft. This enables a modular design of the drive in a particularly simple manner. For example, the drive can have a modular design, in that the pivoted lever and the energy storage unit are part of an energy storage module and are arranged in a first housing section, and the output shaft and/or the electric motor are part of a drive module and are arranged in a separate second housing section that can be connected to the first housing is. Such a modular design has the advantage that the drive can also be used without an energy storage module. Furthermore, the transmission and the energy storage unit can be designed in a particularly simple and cost-effective manner due to the opposing arrangement, without components having to be nested/engaged in one another for reasons of space.

According to one embodiment, the roller and the movable first abutment are mounted on the pivoting lever such that they can rotate about the same axis. This has the advantage that the drive can be manufactured more cost-effectively and the power transmission of the drive power to the energy store and vice versa is optimized when closing.

According to one embodiment, the pivoting lever has a fork-shaped extension, into the free space of which extends a pin on which the movable first abutment is rotatably mounted. As a result, the pivoting lever can be coupled to the movable first abutment in a simple manner and with little friction. The pin can be rotatably mounted on the fork-shaped extension, in particular by means of a ball bearing, cylindrical roller bearing, needle bearing or slide bearing.

According to one embodiment, the movable first abutment has a receptacle for the roller, formed in particular by a fork-shaped extension. The roller can be arranged rotatably in the receptacle, in particular on the aforementioned pin. The roller is preferably rotatably mounted by means of a needle bearing or plain bearing.

According to one embodiment, in the closed position, i.e. in a position of the drive in which the door or the window is closed, the pivot axis of the pivot lever is arranged further away from the output shaft or its center axis than the coupling point, viewed in the direction of a longitudinal extension of the energy store between the pivot lever and the movable first abutment. Preferably, the pivot axis of the pivot lever is offset by about half the distance seen in the direction of the longitudinal extension of the energy storage device, which the first abutment covers when the door or window is fully opened in the direction of the longitudinal extension of the energy storage device. This ensures that the transverse offset of the coupling point between the pivoted lever and the movable first abutment is as small as possible when the pivoted lever is pivoted. Transverse offset here means a movement of the coupling point transverse to the direction of the longitudinal extension of the energy store.

In particular, when the output shaft moves from the closed position to the open position and vice versa, a deflection of the coupling point between the pivoted lever and the movable first abutment perpendicular to the longitudinal axis of the energy store passes through a reversal point. In other words, the coupling point between the pivoted lever and the movable first abutment initially moves away from an imaginary line and then back towards the line during opening or closing, the imaginary line corresponding to the longitudinal axis of the energy store in the closed position.

According to one embodiment, the pivoting lever is curved. This enables a more compact design of the first abutment and of the drive, with a force absorption surface of the first abutment being able to dip into the curvature of the pivoting lever.

According to one embodiment, the energy store is designed as a spring, in particular a compression spring, in particular a spiral compression spring. Alternatively the energy store can be designed, for example, as a set of disk springs or the like.

According to one embodiment, a diameter of the spring is greater than 60% of a housing diameter, preferably greater than 80% of the housing diameter, specifically the housing section surrounding the spring. The housing inner diameter or the housing outer diameter can be regarded as the housing diameter. As a result, a high level of buckling stability is achieved while using as little installation space as possible.

It has been shown that a ratio of the unstressed length of the spring to the diameter of the spring of less than 3 is preferred for the present application. There are particular advantages when the ratio of the unstressed length of the spring to the diameter of the spring is less than or equal to 2. This further improves the buckling stability of the spring.

According to one embodiment, a total number of coils of the spring ranges from X.3 to X.7. The X stands for a natural number. In other words, the beginning of the coils of the spring is offset in the circumferential direction to the end of the coils of the spring. Preferably, the beginning of the coils of the spring and the end of the coils of the spring are at a maximum distance from each other as seen in the circumferential direction. In this case, the total number of coils in the spring is X.5.

According to one embodiment, the ends of the spring are applied and/or ground. The ends can be offset 180° from one another, as is the case with a total number of spring coils of X.5.

According to one embodiment, the spring is held by the two abutments only in its end regions. In other words, the spring is only held in its end areas and thus does not rest on any part in its middle area.

According to one embodiment, the movable first abutment is designed as a spring plate. The spring plate preferably has a front contact surface, i.e. a force absorption surface, for the spring and a holding section which extends into the spring and which can also be referred to as a fixing section.

In general, a force delivered by the energy store for closing the door can be adjustable. A closing force adjustment device is preferably provided, by means of which a prestressing force of the energy store can be adjusted. A distance between the movable first abutment and the second abutment, on which the energy store is supported, can preferably be adjusted by means of the closing force adjustment device. The closing force adjustment device can preferably be operated manually, for example by means of a tool or without tools using an adjustment element.

According to one embodiment, the closing force adjustment device comprises a spindle and a spring plate that can be moved along the spindle by rotating the spindle and forms the second abutment for the energy store. The spring plate is preferably non-rotatably, but axially displaceable, mounted in the housing.

According to one embodiment, the spindle can be driven either directly or via a worm wheel which is rotated by a worm.

The spindle is preferably mounted in the housing such that it can pivot over a defined angular range, preferably by means of a ball joint. This prevents the spindle from jamming when it is rotated in the housing if, due to dimensional deviations that arise during the manufacture of the components, the spring plate and the spindle are arranged at a slight angle to the housing in the assembled state.

According to one embodiment, the cam disk is arranged at least partially in line with the energy store. In particular, the cam disk can be arranged at least partially in alignment with the energy store when the output shaft is in the closed position. The cam disk is preferably arranged with more than 60% of its surface in line with the energy store when the output shaft is in the closed position. As a result, the force can be transmitted directly from the energy store to the cam disk without generating unwanted moments.

According to one embodiment, the central axis of the output shaft is arranged in alignment with the longitudinal axis of the energy store in the closed position. As an alternative to this, the central axis of the output shaft in the closed position can be offset from the longitudinal axis of the energy store by at most the diameter of the roller or the drive shaft. The longitudinal axis of the energy store can intersect the output shaft, preferably a central axis of the output shaft. A central axis, in particular an axis of symmetry, of the cam disk can be positioned parallel to or in the longitudinal axis of the energy store. As an alternative to this, the central axis of the cam disk can run at an angle to the longitudinal axis of the energy store.

According to one embodiment, the pivoting lever is mounted on the housing by means of a ball bearing, a cylindrical roller bearing, a needle bearing or a sliding bearing.

• 1 eine seitliche Darstellung eines erfindungsgemäßen Türantriebs bei geöffnetem Gehäuse;
• 2 eine perspektivische Darstellung des Türantriebs von 1;
• 3A den Türantrieb von 1 in einer Schließstellung der Abtriebswelle in Schnittdarstellung;
• 3B den Türantrieb von 1 in einer Offenstellung der Abtriebswelle in Schnittdarstellung;
• 4 einen Türantrieb gemäß einer zweiten Variante in einer Schließstellung der Abtriebswelle in Schnittdarstellung;
• 5A eine Schnittdarstellung des Türantriebs von 1;
• 5B eine Ansicht auf ein erstes Ende der Druckfeder des Türantriebs von 1;
• 5C eine Ansicht auf ein zweites Ende der Druckfeder des Türantriebs von 1;
• 6A eine perspektivische Ansicht einer Koppelstelle zwischen Schwenkhebel und beweglichem ersten Widerlager gemäß einer ersten Variante;
• 6B eine perspektivische Ansicht einer Koppelstelle zwischen Schwenkhebel und beweglichem ersten Widerlager gemäß einer zweiten Variante;
• 7A eine Schnittansicht eines beweglichen ersten Widerlagers; und
• 7B eine Schnittansicht eines zweiten Widerlagers.

The invention is described below using purely exemplary embodiments with reference to the accompanying drawings. Show it:

• 1 a side view of a door drive according to the invention with the housing open;
• 2 a perspective view of the door drive of 1 ;
• 3A the door drive from 1 in a closed position of the output shaft in a sectional view;
• 3B the door drive from 1 in an open position of the output shaft in a sectional view;
• 4 a door drive according to a second variant in a closed position of the output shaft in a sectional view;
• 5A a sectional view of the door drive from 1 ;
• 5B a view of a first end of the compression spring of the door drive of 1 ;
• 5C a view of a second end of the compression spring of the door drive of 1 ;
• 6A a perspective view of a coupling point between pivot lever and movable first abutment according to a first variant;
• 6B a perspective view of a coupling point between pivot lever and movable first abutment according to a second variant;
• 7A a sectional view of a movable first abutment; and
• 7B a sectional view of a second abutment.

In the 1 and 2 an exemplary embodiment of a door operator 10 according to the invention is shown. The door drive 10 includes an electric motor 18, which is coupled to an output shaft 14 via a transmission 20, so that a drive torque generated by the electric motor 18 is transmitted to the output shaft 14 in order to pivot a linkage (not shown) coupled to the output shaft 14 in such a way that a coupled with the linkage door leaf is transferred from a closed position to an open position. The gear 20 is in this case designed as a reduction gear, ie the torque provided by the electric motor 18 is increased by the gear 20 , while the speed provided by the electric motor 18 is reduced by the gear 20 . For this purpose, the transmission 20 includes a worm gear stage 40 and several, here two, spur gear stages 42 with preferably helical spur gears.

The output shaft 14 is non-rotatably connected to a cam disk 16, a symmetrical cam disk 16 in the present example. An outer peripheral surface 16a (see 2 ) of the cam disk 16 rests against an outer peripheral surface 22a of a roller 22, so that the roller 22 can roll on the outer peripheral surface 16a of the cam disk 16 during operation.

The roller 22 is rotatably attached to a pivot lever 24 . The pivoting lever 24 , which is curved due to the installation space, is in turn attached to a housing 12 of the door drive 10 so that it can pivot about a pivot axis 26 . In addition to the roller 22, a first abutment 34 for an energy store 32 in the form of a spiral compression spring is also attached to the pivot lever 24, more precisely at a coupling point 38 between the pivot lever 24 and the roller 22. The first abutment 34 is pivoted on the pivot lever 24 about an axis 44 which is also the central axis of the roller 22 .

In addition, the door drive 10 has a second abutment 36 for the compression spring 32 . The compression spring 32 is thus arranged between the first abutment 34 and the second abutment 36 . While the first abutment 34, guided by the pivot lever 24, can be pivoted about the pivot axis 26, the second abutment 36 is connected to the housing 12 in a stationary manner, with the exception of a small compensating movement, which will be explained below, so that the second abutment 36 can support a clamping force applied by the first abutment 34 to the compression spring 32 in order to clamp the compression spring 32 . In order to be able to adjust the size of the tensioning force absorbed by the compression spring 32 during the opening of the door, a closing force adjustment device 52 is provided, which with respect to FIG 7B is described in more detail.

As in 1 can be seen, the motor 18 and the gear 20 are arranged on one side of the output shaft 14 and an energy storage unit 28, the first abutment 34, the energy storage 32, the second abutment 36 and - if present - the closing force adjustment device 52 is arranged on a side of the output shaft 14 opposite the motor 18 and the transmission 20 . This simplifies the design and manufacture of the door operator 10 and allows for a modular design so that the door operator 10 can also be manufactured and sold without the energy storage unit 28 .

In the 3A and 3B shows how the energy storage unit 28 is activated, ie how the energy storage device 32 is charged. In 3A the door operator 10 is shown in its closed position S. The roller 22 bears against a concave area 17 of the cam disk 16 which is at a relatively short distance from a central axis 64 of the output shaft 14 . The closing force adjustment device 52 is usually adjusted in such a way that the energy store 32 presses on the roller 22 in the closed position S with a relatively small force and thus holds the roller 22 in the concave region 17 of the cam disk 16 .

When the electric motor 18 drives the output shaft 14 to open the door leaf, the cam disk 16 is rotated relative to the housing 12 (see arrow in Fig 3B) . Since the effective distance between the central axis 64 and the peripheral surface 16a of the cam disk 16 increases as a result of the rotation of the cam disk 16, the roller 22 is displaced by the cam disk 16, ie by the central axis 64 of the cam disk, while it rolls on the peripheral surface 16a 16 pushed away.

Since the roller 22 is attached to the pivot lever 24 so that it can pivot about the pivot axis 26 , the roller 22 moves along a circular path while the roller 22 is displaced by the cam disk 16 . Together with the roller 22, the first abutment 34 also moves on the circular path away from the central axis 64 of the output shaft 14 and towards the second abutment 36. As a result, the energy store 32 designed as a compression spring is compressed and thus tensioned. In order to avoid buckling of the compression spring 32, this has a ratio between the unstressed length of the compression spring and the diameter of the compression spring of less than 2. In addition, the pivot axis 26 of the pivot lever 24 is offset relative to the position of the coupling point 38 between the pivot lever 24 and the first abutment 34 in the closed position S in the direction of the second abutment 36, i.e. to the right in the figures. As a result, the coupling point 38 initially moves away from the center axis 30 of the energy store 32 formed in the closed position S during the pivoting of the pivot lever 24, but approaches it again after a vertex of the center axis 30 has been exceeded, so that the first abutment 34 as a whole moves as far as possible slight offset in the transverse direction, i.e. away from the central axis 30. In addition, the pivot axis 26 is arranged as far away as possible from the central axis 30 in the housing 12 in order to obtain the largest possible pivot radius and thus a small offset in the transverse direction.

The potential energy stored by the energy store 32 can be used to close the door leaf coupled to the door drive 10, for example in the event of a fire. To move the door drive from its open position O ( 3B) back to the closed position S ( 3A) to adjust, the energy storage device 32 presses on the first abutment 36, from which the force is transmitted directly to the cam disk 16 via the roller 22. The roller 22 presses on the cam disk 16, as a result of which the cam disk 16 is set in rotation and a torque is thus generated on the output shaft 14 in order to pivot the door leaf.

While in the embodiment of 3A and 3B the central axis 64 of the output shaft 14 in the closed position S is aligned with the central axis 30 of the energy store 32, with the result that different torque curves result for the door drive 10 depending on the direction of rotation of the output shaft 14, is in 4 In the alternative exemplary embodiment shown, the central axis 64' of the output shaft 14' in the closed position S is offset relative to the central axis 30' of the energy store 32`. In addition, the cam disk 16' is aligned in such a way that its axis of symmetry 66' is arranged at an angle to the central axis 30' of the energy store 32'. This exemplary embodiment has the advantage that almost identical torque curves result in the different directions of rotation.

In 5A is another sectional view of the door operator 10 to see the door operator 10 along the central axis 30 of FIG 3A and perpendicular to the cutting plane according to 3A is shown cut. It is in 5A Among other things, it can be seen that a pin 48 is provided for coupling the roller 22 to the first abutment 34 and the pivoting lever 26 . This sectional view also shows that the roller 22 is rotatably mounted on the pin 48 by means of a needle bearing 68 .

In connection with the 5B and 5C , which represent the two end faces of the compression spring 32, it can also be seen that the ends of the compression spring 32 have been applied and ground and are arranged offset from one another by 180°. In other words, the total number of turns of the compression spring 32 is not an integer, but ends at approximately X.5 turns, where X is a natural number.

In the 6A and 6B two different exemplary embodiments for the coupling point 38 between the rocker arm 24, the roller 22 and the first abutment 34 are shown. The two exemplary embodiments have in common that the pivoting lever 24 has a fork-shaped extension 46, in the intermediate space of which the roller 22 is arranged. The pin 48 for mounting the roller 22 extends parallel to the pivot axis 26 of the pivot lever 24 from one section of the fork-shaped extension 46 to the other section of the fork-shaped extension 46. The two different exemplary embodiments differ, among other things, in how a receptacle 50 of the first abutment 34 is designed. While in accordance with the embodiment 6A the receptacle 50 is formed by a fork-shaped section with two separate holding plates, the receptacle 50 in the exemplary embodiment according to FIG 6B formed by a receptacle 50 enclosing the roller 22 from four sides.

7A shows a detailed view of the coupling point 38 and the first abutment 34 5A . With regard to the coupling point 38, it can be seen here that the pin 48 is rotatably mounted on the pivoted lever 26 via a roller bearing 69, for example a needle bearing. As an alternative to the roller bearing 69, a plain bearing can be provided. In addition, 7A It can be seen that the first abutment 34 has, in addition to the receptacle 50 for coupling the abutment 34 to the pin 48 , a front force absorption surface 70 and a radial fixing section 72 . The radial fixing section 72 engages in the compression spring 32 at the front in order to support the compression spring 32 radially.

7B shows a detailed view of the second abutment 36 and the closing force adjustment device 52 connected to the second abutment 36. The second abutment 36 has—a mirror image of the first abutment 34—a frontal force absorption surface 74 and a radial fixing section 76. In addition, the second abutment 36 has two opposite extensions 78 (cf. 2 ), which engage in corresponding recesses in the housing 12 in such a way that the second abutment 36 is arranged in the housing 12 secured against rotation. The second abutment 36 also has a threaded opening 80 whose internal thread meshes with a spindle 54 . The spindle 54 is in turn connected in a rotationally fixed manner to a worm wheel 58, which can be set in rotation from the outside via a worm 60 (cf. 2 ). The second abutment 36 can be axially displaced by rotating the spindle 54 so that the compression spring 32 can be tensioned or relaxed. So that the second abutment 36 can perform a compensating movement while the first abutment 34 moves along the circular path, i.e. it can adapt to the slightly changing axial alignment of the compression spring 32, the spindle 54 can be pivoted on the housing 12 by means of a ball joint 62 , Here a housing cover 12a stored. The ball joint 62 is therefore used to ensure that the spindle 54 is automatically aligned in the direction of the central axis 30 of the compression spring and that the compression spring 32 is thus always held securely between the two abutments 34, 36 without having to provide an additional bearing for the compression spring 32. The ball joint 62 can also serve to compensate for manufacturing tolerances. If no closing force adjustment device is provided, the second abutment 36 can nevertheless be arranged in the housing such that it can pivot over an angular range, for example via a ball joint.

Overall, it is noticeable in the present design that the first abutment 34 is mounted guided solely by the pivoted lever 24 and therefore does not require a linear bearing. It is also noticeable that the compression spring 32 is held in position only by the two abutments 34, 36 and is therefore installed in the door drive 10 in a quasi “floating” manner. As a result, particularly little friction is generated during operation of the door drive 10, which makes the door drive 10 efficient and low-maintenance.

Reference List

10

drive

12

Housing

12a

housing cover

14

output shaft

16

cam disk

16a

outer peripheral surface

17

concave area

18

electric motor

20

transmission

22

roller

22a

outer peripheral surface

24

swing lever

26

pivot axis

28

energy storage unit

30

longitudinal axis

32

energy storage

34

first abutment

36

second abutment

38

coupling point

40

worm gear

42

spur gear

44

axis

46

fork-shaped extension (pivoting lever)

48

Pen

50

Recording

52

Closing force adjustment device

54

spindle

58

worm wheel

60

Snail

62

ball joint

64

central axis

66

axis of symmetry

68

needle bearing

69

roller bearing

70

force absorbing surface

72

fixing section

74

force absorbing surface

76

fixing section

78

extension

80

threaded opening

S

closed position

O

open position

Claims (23)

Drive (10) for a door or a window, comprising a housing (12), an output shaft (14) rotatably mounted on the housing (12) with a cam disk (16), an electric motor (18) with a gearbox (20) for driving the output shaft (14) from a closed position (S) in an opening direction in order to open the door or the window, a roller (22) rolling on the rotating cam disk (16) during operation, a pivot lever (24) which is articulated on the housing (12) pivotably about a pivot axis (26), the roller (22) being arranged rotatably on the pivot lever (24), and an energy storage unit (28) for driving the output shaft (14) from an open position (O) in a closing direction in order to close the door or the window, the energy storage unit (28) having an energy storage device (32) having a longitudinal axis (30) and a has a movable first abutment (34) facing the roller (22) and a second abutment (36) facing away from the roller (22), on which the energy store (32) is supported, the roller (22) acting in a force-transmitting manner between the cam disk (16) and the movable first abutment (34) of the energy storage unit (28), wherein the cam disc (16) and the energy storage unit (28) are arranged on opposite sides of the pivot lever (24), and the movable first abutment (34) of the energy storage unit (28) being rotatably and non-displaceably coupled to the pivoted lever (24) at a coupling point (38) and thereby guided by the pivoted lever (24) on a circular path. Drive (10) after claim 1 , characterized in that the gear (20) comprises a worm gear (40) and a spur gear (42). Drive (10) after claim 1 or 2 , characterized in that the electric motor (18) and the energy storage unit (32) are arranged on opposite sides with respect to the output shaft (14). Drive (10) according to one of the preceding claims, characterized in that the roller (22) and the movable first abutment (34) are mounted on the pivoting lever (24) so as to be rotatable about the same axis (44). Drive (10) according to one of the preceding claims, characterized in that the pivoting lever (24) has a fork-shaped extension (46) into whose free space extends a pin (48) on which the movable first abutment (34) is rotatably mounted . Drive (10) according to one of the preceding claims, characterized in that the movable first abutment (34) has a receptacle (50), formed in particular by a fork-shaped extension, for the roller (22) and the roller (22) being rotatable in the receptacle (50) is arranged. Drive (10) according to one of the preceding claims, characterized in that in the closed position (S) the pivot axis (26) of the pivot lever (24) is arranged further away from the output shaft (14) viewed in the direction of a longitudinal extension of the energy store (28). as the coupling point (38) between the pivoting lever (24) and the movable first abutment (34). Drive (10) according to one of the preceding claims, characterized in that when the output shaft (14) moves from the closed position (S) to the open position (O) and vice versa, a deflection of the coupling point (38) between the pivoted lever (24) and the movable first abutment (34) perpendicular to the longitudinal axis (30) of the energy store (32) passes through a reversal point. Drive (10) according to one of the preceding claims, characterized in that the pivoted lever (24) is curved. Drive (10) according to one of the preceding claims, characterized in that the energy store (32) is designed as a spring, in particular a compression spring, in particular a spiral compression spring. Drive (10) after claim 10 , characterized in that a diameter of the spring (32) is greater than 60% of a housing diameter, preferably greater than 80% of the housing diameter. Drive (10) after claim 10 or 11 , characterized in that a ratio of the unstressed length of the spring to the diameter of the spring is less than 3, in particular less than 2. Drive (10) according to at least one of Claims 10 until 12 , characterized in that a total number of turns of the spring is in the range between X.3 to X.7, in particular X.5, where X is a natural number. Drive (10) according to at least one of Claims 10 until 13 , characterized in that the ends of the spring (32) are applied and/or ground and/or offset by 180° to one another. Drive (10) according to at least one of Claims 10 until 14 , characterized in that the spring (32) is held exclusively in its end areas by the two abutments (34, 36). Drive (10) according to at least one of Claims 10 until 15 , characterized in that the movable first abutment (34) is designed as a spring plate. Drive (10) according to one of the preceding claims, characterized in that a closing force adjustment device (52) is provided, by means of which a pretensioning force of the energy store (32) can be adjusted. Drive (10) after Claim 17 , characterized in that the closing force adjustment device (52) comprises a spindle (54) and a spring plate which can be moved along the spindle (54) by rotating the spindle (54) and forms the second abutment (36) for the energy store (32). Drive (10) after Claim 18 , characterized in that the spindle (54) can be driven either directly or via a worm wheel (58) which is rotated by a worm (60). Drive (10) after Claim 18 or 19 , characterized in that the spindle (54) is pivotably mounted in the housing (12) over a defined angular range, in particular by means of a ball joint (60). Drive (10) according to one of the preceding claims, characterized in that the cam disk (16) is arranged at least partially in line with the energy store (32). Drive (10) according to one of the preceding claims, characterized in that in the closed position (S) the central axis (64) of the output shaft (14) is arranged in alignment with the longitudinal axis (30) of the energy store (32) or that in the closed position (S) the central axis (64) of the output shaft (14) is arranged offset to the longitudinal axis (30) of the energy store (32) by at most the diameter of the roller (22) or drive shaft (14). Drive (10) according to one of the preceding claims, characterized in that the pivoting lever (24) is mounted on the housing (12) by means of a ball bearing, a needle bearing or a plain bearing.

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